US4500300A - Rotationally elastic coupling - Google Patents

Rotationally elastic coupling Download PDF

Info

Publication number
US4500300A
US4500300A US06/445,386 US44538682A US4500300A US 4500300 A US4500300 A US 4500300A US 44538682 A US44538682 A US 44538682A US 4500300 A US4500300 A US 4500300A
Authority
US
United States
Prior art keywords
half coupling
rotationally elastic
bearing
coupling
elastic coupling
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US06/445,386
Other languages
English (en)
Inventor
Franz-Josef Wolf
Hubert Pletsch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Woco Franz Josef Wolf and Co GmbH
Original Assignee
Woco Franz Josef Wolf and Co GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Woco Franz Josef Wolf and Co GmbH filed Critical Woco Franz Josef Wolf and Co GmbH
Assigned to WOCO FRANZ-JOSEF WOLF & CO. reassignment WOCO FRANZ-JOSEF WOLF & CO. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: PLETSCH, HUBERT, WOLF, FRANZ-JOSEF
Application granted granted Critical
Publication of US4500300A publication Critical patent/US4500300A/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/60—Clutching elements
    • F16D13/64—Clutch-plates; Clutch-lamellae
    • F16D13/68—Attachments of plates or lamellae to their supports
    • F16D13/686—Attachments of plates or lamellae to their supports with one or more intermediate members made of rubber or like material transmitting torque from the linings to the hub
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F16D3/76—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members shaped as an elastic ring centered on the axis, surrounding a portion of one coupling part and surrounded by a sleeve of the other coupling part

Definitions

  • the invention concerns a rotationally elastic coupling in which the two half couplings are connected with one another by at least one sprung intermediate link.
  • Couplings of this type provide for the rotationally elastic transmission of torques between two shafts, in particular coaxial shafts.
  • Rotationally elastic couplings of the type being discussed generally consist of concentrically arranged half couplings with alternately arranged interlacing or overlapping claws, supports or end stops between which sprung intermediate links are placed.
  • These sprung intermediate links generally consist of an elastomer and are embodied, in particular, in the form of elastic tensile ties, in the form of struts, in the form of buffers and also in the form of annular bulges or beaded discs.
  • a disadvantage of all the known rotationally elastic couplings of this type is the fact that the sprung angle between the two half couplings is too small and that the sprung intermediate links are loaded in both compression and tension or exclusively in shear, such load reversals leading rapidly to irreversible material fatigue, particularly where an elastomer is used as the material for the sprung intermediate links.
  • "Sprung angle” is taken to mean the maximum angle of twist through which the two half couplings can be rotated relative to one another giving a sprung and damping action within a sensibly usable working range.
  • a rotationally elastic coupling of the type mentioned at the beginning is also known from U.S. Ser. No. 146,253 of May 5th 1980, now abandoned, in which the sprung intermediate links consisting of an elastomer are only put under compression independent of the rotational direction of the transmission half coupling; however, even with this rotationally elastic coupling, the sprung angle is only a few degrees.
  • This known rotationally elastic coupling in common with all other known rotationally elastic couplings, does not provide a spring characteristic extending beyond a sprung angle range of 15° or 20°.
  • the known rotationally elastic couplings Using the known rotationally elastic couplings, the load reversal impact torques occurring at low rotational speeds or with strictly driving techniques cannot be absorbed and these lead to load reversal vibrations in the longitudinal direction of the vehicle. Furthermore, the resonant vibrations occurring in the longitudinal direction of motor vehicles cannot be subcritically decoupled using the known rotationally elastic couplings. For this reason, the known rotationally elastic couplings with twist angle characteristics or sprung angles of up to a maximum of 20° are only used for obviating transmission noise in motor vehicles but are not tuned to damp out the load reversal impact torques.
  • the invention is base on the task of producing a rotationally elastic coupling with a longer operating life and making possible the use of a twist angle characteristic or a sprung angle of much more than 20°, in particular up to more than 90°.
  • the invention produces a rotationally elastic coupling of the type mentioned at the beginning having the characteristics important to the invention.
  • the basic idea of the invention is thus to replace the mainly tangential or secantial compressive or shear load on the sprung intermediate links located between the half couplings by an at least mainly radial and translational load on the sprung intermediate links using a conversion of the relative twist between the two half couplings via a convertor of movement direction, for example an eccentric.
  • the conversion of a relative twist between the two preferably mutually coaxial half couplings into an at least substantially translational radially inwards or outwards component of force and movement, to which the sprung intermediate links are subjected, can occur in principle by means of crank links or eccentric links, for example, and preferably occurs by means of an eccentric link.
  • This eccentric link is embodied in particular as an eccentric disc or as a group of axial eccentric discs in series, which is or are connected eccentrically or rotationally solidly with one half coupling and are supported or are carried or guided with sliding or rotational freedom on at least one or several of the sprung intermediate links, of which each is preferably associated with one eccentric disc.
  • the sprung intermediate links are preferably manufactured from reinforced or unreinforced elastomer but can also be made from sprung steel and, for example, have the form of helical springs, elliptical springs or specially adapted shaped leaf springs.
  • the compressive loading capability of the elastomer can be increased in a manner known per se by vulcanizing in sheet metal components to prevent lateral extension.
  • the coupling is constructed to be coaxial and concentric with respect to the two half couplings, the sprung intermediate links are preferably embodied in the form of at least substantially cylindrical curved shell elements.
  • Each of these rubber-elastic shell elements is rotationally solidly connected with one of the half couplings by means of one of its cylindrical curved outer surfaces and may, for example, be screwed, glued and/or vulcanized onto the latter, preferably attached by matching shapes, in particular attached by insertion in the axial direction, or clipped on and connected by its other cylindrical outer surface with a support or bearing element, in which the link converting the rotation into a radial translation or vice versa, i.e. the eccentric link, for example, of the other half coupling is supported or with which the latter makes contact.
  • the softer the spring characteristic of the sprung intermediate links for a given eccentricity of the eccentric link the greater will be the twist angle which will appear for a given torque magnitude in the torque equilibrium. Again, the greater this twist angle is in the range of torque equilibrium, the softer will be the torque transmission behaviour of the coupling in the torque/twist angle characteristic, i.e. the spring characteristic of the rotationally elastic coupling.
  • the eccentric geometry and the spring characteristics of the sprung intermediate links will preferably be designed so that the maximum torque which is to be expected under normal operating conditions and to which the coupling will be subjected will produce a twist angle in the range from approximately 60° to 100°.
  • the angular displacement (from approximately 80° to 120°) remaining between the twist angle tuned and set in this manner and the maximum possible sprung angle of 180° is then available for ensuring soft and shock-free overload protection.
  • a coupling which is designed for a twist angle of 90° with the maximum torque of normal operation, can without difficulty be subjected to suddenly occurring substantially greater torques than the maximum to be expected in normal operation without this leading to bumps, shocks or rupture in the driven shaft because such torsional impacts are taken up by the rotationally elastic coupling with a soft progression of the characteristic but without bottoming up to a sprung angle of 180°, i.e. twice the amount of the normal maximum twist angle of 90° considered in this example. If torques are introduced to the coupling which even exceed this safety range, only "slipping" of the coupling then occurs.
  • the sprung intermediate links are progressively unloaded (ignoring the possible occurrence of some trivial shear forces) and this continues until the two half couplings have completed a relative twist of 360°, referred to the unloaded zero position of the coupling; at this point, increasing radial loading of the sprung intermediate links appears again, which is characteristic of the normal operation of the coupling.
  • the rotationally elastic coupling in accordance with the invention in the embodiment described above thus provides an absolutely operationally safe overload protection for the force transmission in which bottoming and damage cannot occur and which may be described as ideal.
  • end stop means such end stop means limiting either the radial sprung path of the sprung intermediate links or the relative twist of the two half couplings relative to one another by means of claw stops.
  • Such end stop means are desirable in cases in which a vertical end to the spring characteristic of the coupling is not damaging and/or is acceptable and should or must be operated in favour of larger sprung angle ranges for normal operation with smaller reserve ranges of the twist angle.
  • end stop means are preferably provided when the coupling is, for example, designed for a sprung angle of 170° for the maximum torques expected during normal operation. For safety reasons also, it is often necessary to prevent slipping of the coupling by end stop means.
  • any other movement-converting intermediate link can finally, in principle, be used provided there is a guarantee that such a movement-converting intermediate link converts a relative twist of the half coupling to which it is connected (relative to the other half coupling) into an at least substantially radially directed translational force component and movement component.
  • the most varied extension mechanisms could, for example, be used for this conversion. In this connection, the choice among the elements available in principle depends primarily also on the magnitude of the forces to be transmitted.
  • the sprung intermediate links can be arranged in the unloaded coupling with either negative or positive prestressing or without prestressing.
  • negative prestressing for example, is meant a tensile prestressing of the spring element where this is loaded compressively.
  • a tensile prestressing of the spring element would be a positive prestressing if the spring element has a tensile loading during normal operation of the coupling.
  • the type of prestressing or, in some cases, the use of unstressed sprung intermediate links depends in each case on the requirements of the individual application or, more precisely, on the spring characteristic expected from the coupling for the individual case.
  • a mass produced coupling is to be applied with varying tuning for different purposes, this can be achieved in a particularly advantageous manner if the sprung intermediate links, for example elastomer bodies, are enclosed in a surrounding cage which is part of the half coupling or is connected to it by shaped fitting, the diameter of this cage being variable within the desired ranges by means of appropriate tensioning and de-tensioning means.
  • the sprung intermediate links for example elastomer bodies
  • a particular coupling is designed for transmitting a torque of 100 Nm at a twist angle of 90° and the same coupling has to transmit a torque of 130 Nm, for example, with the same spring angle of 90°, then it is only necessary with a coupling designed as a cage coupling of this type to more tightly tension the cage surrounding and prestressing the sprung intermediate links in order to meet these conditions.
  • the torque/twist angle characteristic i.e. the spring characteristic of the coupling
  • the spring elements are designed as exchangeable elements shaped fixedly in the rotational direction and insertable in the axial direction for half couplings arranged concentrically in a radial plane; in particular, the elements may be rubber-metal springs with at least one radially outer and one radially inner metal plate holding the spring element.
  • the characteristics can be chosen and adapted at will by various combinations of such individual elements and, in particular, can also be different in the two opposed rotational directions of the relative twist of the two half couplings.
  • the rubber-metal springs can, in principle, have any given shape according to the particular knowledge of this field of constructional technology.
  • the elastomer cross-section of the rubber springs in the axial direction can, for example, be substantially rectangular, V-shaped with apex pointing either inwards or outwards or be provided with one or more internal spaces or damping spaces.
  • the elastomer of the rubber spring when such is used as the sprung intermediate link of the coupling, will preferably be put under compression during normal operation. This causes the elastomer to form annular bulges in the axial direction which, under certain circumstances, for particular applications--for example in heavy vehicles--can lead to an excessively "soft" spring characteristic of the coupling, i.e. to an excessively weak progression of the transmitted torque as a function of the twist angle. This situation can, if required, be corrected, i.e.
  • the spring characteristic can be stiffened and hence become progressively stronger if the coupling or at least the unloaded annular rubber surfaces of the rubber springs or rubber-metal springs lying axially sidewards in the radial plane are enclosed by sheet metal on both sides in the form of a capsule or a cage. This encapsulation can then occur such that in the unloaded condition of the coupling, i.e. without work being fed into the coupling, the side annular surfaces of the rubber springs are at a certain distance from the sheet metal on the side of the cage or, alternatively, are in direct contact with the inner wall of the sheet metal of the cage.
  • the coupling produces first a soft characteristic and then, after the bulging rubber comes into contact with the sheet metal of the cage, a progressively steepening characteristic; in the second case, an initially steep, i.e. strongly progressive characteristic of the coupling is produced by a reduction of the freely deformable unloaded surface of the rubber spring.
  • an initially steep, i.e. strongly progressive characteristic of the coupling is produced by a reduction of the freely deformable unloaded surface of the rubber spring.
  • removable and exchangeably connected rubber spring elements with varying Shore hardnesses and varying geometric shapes and, in particular, distances from the internal walls of the capsule sheet metal or the cage sheet metal, a practically unlimited multiplicity and fine adjustment of the desired coupling spring characteristics for any particular case can be obtained.
  • Such an enclosed encapsulation of the spring elastomer limited on all sides can also make it possible to set and obtain such a strongly progressive variation of the spring characteristic that this can also be designed as the end stop and hence a higher twist angle of the coupling can be used.
  • the lining carrying plate can be arranged in one piece with one of the two sheet metal parts forming the sidewards encapsulation of the coupling; this then operates simultaneously as the centering element and can be pressed directly onto the central sleeve of the clutch and, for example, be retained by a circlip.
  • the eccentric link is generally so arranged and directed that it is in its dead centre position when the coupling is unloaded. With this zero position of the eccentric for the unloaded coupling, the full 180° of useful sprung angle is available in both rotational directions.
  • a typical characteristic of the eccentric geometry is that with initial twist of the eccentric from its dead centre position, this twist is only converted into a very short translational displacement path.
  • the eccentric can be so set and arranged that with the coupling unloaded it is deflected from its dead centre position by an angle which is prescribed by and depends on the particular requirements of the individual application.
  • Such deflection from the zero position of the coupling out of the dead centre position of the eccentric can take place in either the positive or the negative direction.
  • the determination of the deflection of the zero position from the dead centre of the eccentric can, in principle, occur in any given and known manner, for example by an appropriately twisted arrangement of the bearing carrying the eccentric, which is connected with the sprung intermediate links.
  • the rotationally elastic coupling is preferably so designed that the input and output are coaxial.
  • the rotationally elastic coupling according to the invention is characterised by an unusually large degree of adaptability, namely with respect to the twist angles to be set, the torques to be transmitted and also the size of the construction. Because of these properties, the rotationally elastic coupling in accordance with the invention can be applied in practically any given field of technology wherever torques have to be transmitted rotationally elastically.
  • the coupling can be applied particularly as a damping link in propulsion systems, serving at the same time as an effective overload protection.
  • the rotationally elastic coupling according to the invention is currently most important in motor vehicles where it can be applied particularly to the damping of impact torques at low and extremely low engine speeds.
  • the rotationally elastic coupling in accordance with the invention can, in this connection, be applied with particular advantage in the currently used clutches in motor vehicles and, in particular, between the clutch plate of the clutch and the output shaft of the clutch or input shaft of the gear box.
  • Driving tests carried out by the applicant have shown that using motor cars currently commercially available, it is possible to drive away smoothly in 4th gear, i.e. at large conversion ratios, even if the usual lining springs for currently conventional clutches are removed.
  • the rotationally elastic coupling according to the invention will preferably continue to be applied as a suppressor, particularly a low frequency suppressor in motor vehicles.
  • FIG. 1 shows an axial end view of an illustrative example of the rotationally elastic coupling
  • FIG. 2 shows a section along II--II in FIG. 1;
  • FIG. 3 shows a modified illustrative example of the rotationally elastic coupling in accordance with FIG. 1;
  • FIG. 4 shows a further illustrative example of the rotationally elastic coupling
  • FIG. 5 shows an illustrative example of the rotationally elastic coupling in an axial end view of the type of FIG. 1 with axially insertable rubber springs;
  • FIG. 6 shows an illustrative example of the rotationally elastic coupling with rubber springs in a partial axial section corresponding to FIG. 2 in the unloaded and in the loaded condition with metal sheet encapsulation on both sides;
  • FIG. 7 shows, in an axial partial section, a profile of the rubber spring of the rotationally elastic coupling deviating from the rectangular shape
  • FIG. 8 shows a further profile of the rubber spring of the rotationally elastic coupling in a representation corresponding to FIG. 7;
  • FIG. 9 shows an illustrative example of the rubber spring of the rotationally elastic coupling in which the rubber spring is divided axially into two symmetrical elements.
  • FIGS. 1 and 2 show an illustrative example of the rotationally elastic coupling as part of a clutch for motor vehicles.
  • the clutch plate 1 with the clutch linings 2 is rotationally solidly connected to a cylindrical steel ring which forms one half coupling 3 of the rotationally elastic coupling.
  • Two diametrically opposed elastomer bodies 4, 5 are rotationally solidly vulcanized onto the inner side of the annular half coupling 3; these elastomer bodies serve as sprung elastic intermediate links of the rotationally elastic coupling.
  • the elastomer bodies 4, 5 have at least substantially the shape of cylindrical half shells and, to increase their form factor, i.e. to increase the shape stiffness by preventing lateral extension under compressive load, are each provided with an enclosed sheet metal part 6, 7.
  • the gear box shaft sleeve of the clutch serves as the second half coupling 8 of the rotationally elastic coupling.
  • the second half coupling 8 is rotationally solidly connected with two eccentric discs 9, 10 which, in the illustrative example shown here, are shown in a knife and fork arrangement for reasons of mass balance.
  • the eccentric discs 9, 10 are rotatively supported by means of roller bearings or journal bearings 11, 12 in bearing shells 13, 14, which are solidly connected by vulcanization with the sprung intermediate links 4, 5, in this case with elastomer bodies.
  • the bearings 11, 12 are themselves placed eccentrically in the bearing shells 13, 14 in the manner visible from FIG. 1, in such a way that in the manner also visible from FIG. 1 the zero position of the coupling and the eccentric with the coupling unloaded is rotated out of the dead centre position of the eccentric, referred to the sprung intermediate links 4, 5.
  • FIG. 3 shows, when compared with FIG. 2, a modified illustrative example of the coupling represented in FIGS. 1 and 2.
  • the illustrative example shown in FIG. 3 corresponds to the illustrative example also shown in FIG. 2.
  • the coupling shown in FIG. 3 is not a clutch but a solid coupling through which a torque is transmitted from an input shaft 15 to an output shaft 16 via a solid connection 17.
  • the input shaft 15 is connected with one half coupling 8 and the output shaft 16 via the solid connection 17 with the other half coupling 3.
  • FIG. 4 shows an illustrative example of the rotationally elastic coupling of the type shown in FIG. 1 in which the elastomer bodies 4, 5 shown in FIG. 1 are replaced by steel spring elements and, in detail, by helical springs 18, an elliptical spring element 19 and a specially adapted shaped leaf spring 20.
  • the spring characteristic of the rotationally elastic coupling can be supplemented by an adjustable damping characteristic.
  • the coupling is equipped with several eccentrics, it does not have to have the knife and fork arrangement shown in FIGS. 2 and 3, but the individual eccentric discs with their bearings and sprung intermediate links can be assembled on top of one another in series in knife and fork arrangement and, for example, finally retained in a common cage and then provided with a precalculated mass balance.
  • the coupling is advantageous.
  • FIG. 5 shows an axial end view of a rotationally elastic coupling of the type shown in FIG. 1 in which the sprung intermediate links are embodied as exchangeable elastomer springs 21, 22 and 23.
  • Steel sheets 24, 25, 26, 27, 28, 29 are vulcanized onto the sprung elastomer bodies of each of these elastomer sprung elements on the opposing main surfaces in each case, i.e. radially inward and radially outward referred to the coupling.
  • the edges of these steel sheets protrude beyond the elastomer bodies to which they are vulcanized in the peripheral direction of the coupling.
  • the outer edges 30 and 32 of the external metal sheet 28 of the elastomer spring 23 can for example be moved axially and are held positively in the peripheral direction under the recesses 34, 36, which are positively connected or designed, in one piece in this case, with the radially outer half coupling 3.
  • the edges 31, 33 of the radially inward metal sheet 29 of the elastomer spring 23 are axially displaceable in the recesses 35, 37 and held by shape in the peripheral direction in the bearing shell 14, which is force connected via the bearing 11 and the eccentric 9 with the inner half coupling 8.
  • the elastomer spring 23 it is not, of course, necessary for the elastomer spring 23 to be incorporated as only one large spring as shown at the bottom of FIG. 5.
  • the elastomer springs do not need to consist of a continuous elastomer block between inner and outer retaining metal sheets, as shown in FIG. 5. They can of course, in a manner known per se, contain at least one, as shown for example in the type indicated in FIG. 1, and preferably several intermediate metal sheets which have been vulcanized in, in order to reduce the lateral extension of the springs and increase the shape stiffness in a manner known per se.
  • the illustrative embodiment shown in FIG. 5 has end stop edges 38, 39, which limit the radial displacement path of the bearing shell 14.
  • the rotationally elastic coupling shown in FIG. 1 "slips" on overload and thus, for example, protects engines or driven equipment from overload
  • the rotationally elastic coupling shown in FIG. 5 leads to a solid connection between the input shaft and the output shaft in the direction of the load in the case of overload; this is necessary for safety reasons in many cases, for example in lifts.
  • end stop shown only in the lower part of the coupling in FIG. 5 can, of course, also be provided in addition in the upper part of the coupling so that each of the two bearing shells 13, 14 shown in FIG. 5 is thus radially displaceable to a limited extent by means of end stops.
  • FIG. 6 shows an axial partial section of an illustrative embodiment of the rotationally elastic coupling which differs from the illustrative embodiment shown in FIG. 2 by the encapsulation of the coupling on both end faces.
  • the encapsulation sheets 40, 41 placed on the two opposing end faces and centred on the clutch sleeve 8 serve to limit the deformation of the elastomer layers of the sprung intermediate links 4, 5 in the axial direction under load, thus stiffening the spring characteristic of the rotationally elastic coupling.
  • One of these encapsulating sheets, namely the encapsulating sheet 40 is arranged at the same time to be in one piece with the lining carrier plate 42.
  • the rubber elastic intermediate link 5 is shown with full lines in the unloaded condition while the loaded deformed condition occurring when the coupling is loaded and which is caused by the compressive load on the intermediate link in the radial direction, is shown with dotted lines.
  • FIGS. 7, 8 and 9 Three further versions of an encapsulated rotationally elastic coupling are shown in FIGS. 7, 8 and 9 in a representation corresponding to that of FIG. 6. They differ from the illustrative embodiment shown in FIG. 6 by the differing profile of the elastomer springs 43 (FIG. 7), 44 (FIG. 8) and 45 (FIG. 9).
  • the two elastomer springs differ substantially in the fact that the elastomer spring 43 in the unloaded condition of the coupling shown in FIG. 7 lies well away from the encapsulating sheets 40, 41 whereas the elastomer spring 44 shown also in the unloaded condition in FIG. 8 is in contact with the encapsulating sheets 40, 41.
  • the coupling shown in FIG. 7 has an angle pointing radially outwards and the elastomer spring 44 shown in FIG. 8 has an angle pointing radially inwards
  • the two elastomer springs differ substantially in the fact that the elastomer spring 43 in the unloaded condition of the coupling shown in FIG. 7 lies well away from the encapsulating sheets 40, 41 whereas the elastomer spring 44 shown also in the unloaded condition in FIG. 8 is in contact with the encapsulating sheets 40, 41.
  • the elastomer spring 43 can deform initially in the axial direction without resistance until the point is reached when the elastomer comes into contact with the encapsulating sheets 40, 41. Only then is further deformation prevented leading to a steeper progression of the spring characteristic of the coupling, i.e. to a "stiffening" of the coupling after an initially soft spring characteristic.
  • the coupling shown in FIG. 8 has a relatively strongly progressive variation of the spring characteristic of the coupling right from the beginning.
  • FIG. 8 shows an illustrative embodiment of the rotationally elastic coupling which, in comparison with the coupling shown in FIG. 7, has a strongly progressive spring characteristic right from the beginning
  • the rotationally elastic coupling shown in FIG. 9 has, at the beginning, an even softer initiation of the spring characteristic, i.e. an even flatter variation of the torque as a function of the twist angle than is the case with the illustrative embodiment shown in FIG. 7.
  • the elastomer spring 45 FIG. 9 when subjected to compression in the radial direction can deform both axially inwards and axially outwards. Due to the contact of the two part springs with one another in the axially inward direction and with the encapsulating sheets 40, 41 in the axially outward direction, the spring characteristic of the rotationally elastic coupling shown in FIG. 9 then also becomes strongly progressively.
  • the lining carrier plate 42 need not be arranged as a flat annular disc (as shown here for simplicity) but can quite easily also be arranged in a manner known per se to be corrugated as a lining carrier spring. It is also open to the expert to apply as required known and conventional pre-dampers in association with the rotationally elastic coupling in accordance with the invention.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Joints Allowing Movement (AREA)
  • Road Signs Or Road Markings (AREA)
  • Confectionery (AREA)
  • Springs (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Transmission Devices (AREA)
US06/445,386 1982-03-26 1982-11-29 Rotationally elastic coupling Expired - Fee Related US4500300A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19823211238 DE3211238A1 (de) 1982-03-26 1982-03-26 Drehelastische kupplung
DE3211238 1982-03-26

Publications (1)

Publication Number Publication Date
US4500300A true US4500300A (en) 1985-02-19

Family

ID=6159425

Family Applications (1)

Application Number Title Priority Date Filing Date
US06/445,386 Expired - Fee Related US4500300A (en) 1982-03-26 1982-11-29 Rotationally elastic coupling

Country Status (5)

Country Link
US (1) US4500300A (fr)
EP (1) EP0090075B1 (fr)
JP (1) JPS58178025A (fr)
AT (1) ATE20273T1 (fr)
DE (2) DE3211238A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5573463A (en) * 1994-05-20 1996-11-12 Continental Emsco Company Elastomeric drive line coupling for transmitting torque and simultaneously accomodating shaft misalignments and angular deflections
US5697261A (en) * 1993-12-23 1997-12-16 Valeo Damping device for absorbing rotation shocks, and a friction clutch including such a device
EP0992699A3 (fr) * 1998-10-09 2000-11-02 Safe Developments Limited Disque d'embrayage
US20060249470A1 (en) * 2005-05-06 2006-11-09 Voith Turbo Scharfenberg Gmbh & Co. Kg Separable center position coupling
US7426870B2 (en) * 2002-07-15 2008-09-23 Endress + Hauser Gmbh + Co. Kg Torsional fixing device, especially for the housing of a measuring transducer
CN110247522A (zh) * 2018-03-09 2019-09-17 株式会社电装 旋转电机

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3243640A1 (de) * 1982-11-25 1984-05-30 WOCO Franz-Josef Wolf & Co, 6483 Bad Soden-Salmünster Drehelastische kupplung
DE3243644A1 (de) * 1982-11-25 1984-05-30 WOCO Franz-Josef Wolf & Co, 6483 Bad Soden-Salmünster Drehelastische kupplung
DE4025777A1 (de) * 1990-08-15 1992-02-20 Stromag Maschf Verdrehbegrenzung fuer eine wellenkupplung
FR2690959B1 (fr) * 1992-05-07 1994-07-08 Valeo Friction d'embrayage, notamment pour vehicule automobile.

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2833131A (en) * 1954-10-25 1958-05-06 Cooper Bessemer Corp Resilient coupling
US3386264A (en) * 1965-03-30 1968-06-04 Luxembourg Brev Participations Resilient couplings
US4252227A (en) * 1979-08-17 1981-02-24 General Motors Corporation Torsional vibration damper and clutch assembly
US4277958A (en) * 1977-07-29 1981-07-14 Hackforth Gmbh & Co. Kg Flexible shaft coupling
US4368050A (en) * 1980-09-08 1983-01-11 Barry Wright Corporation Coupling
US4380442A (en) * 1980-03-15 1983-04-19 Firma Carl Freudenberg Flexible coupling
US4424046A (en) * 1980-10-06 1984-01-03 Sgf Suddeutsche Gelenkscheibenfabrik, Gmbh & Co. Kg Flexible coupling

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR957151A (fr) * 1950-02-16
US1488740A (en) * 1922-12-23 1924-04-01 Timothy C Dobbins Resilinet universal joint for power transmission
US1704503A (en) * 1927-11-30 1929-03-05 Borg & Beck Co Clutch plate
US1896025A (en) * 1928-03-17 1933-01-31 Packard Motor Car Co Motor vehicle clutch
US1967052A (en) * 1932-04-20 1934-07-17 Edwin J Dumm Vibration cushioning driving device
US2100362A (en) * 1933-11-23 1937-11-30 Thorwald Lillemoen Clutch construction
US2174342A (en) * 1936-03-07 1939-09-26 Frank C Greulich Flexible coupling device
CH187205A (fr) * 1936-03-24 1936-10-31 Gardy Particip App Mécanisme destiné à immobiliser un axe dans des positions déterminées.
US2398261A (en) * 1941-11-24 1946-04-09 Deister Concentrator Company Flexible coupling
US2837902A (en) * 1956-07-12 1958-06-10 Otis L Stevens Mechanical torsional vibration damper
FR1186498A (fr) * 1956-11-16 1959-08-25 Zd Y V I Plzen Narodni Podnik Accouplement élastique articulé
FR1166284A (fr) * 1957-02-12 1958-11-04 Accouplement pour arbres en ligne
US2969657A (en) * 1959-04-27 1961-01-31 Schwitzer Corp Flexible coupling
DE1906295U (de) * 1962-08-25 1964-12-10 Josef Muehlbeyer Maschb Ausgleichskupplung.
FR1604475A (fr) * 1968-01-16 1971-11-08
DE2212468C3 (de) * 1972-03-15 1979-05-31 Alfred Teves Metallwarenfabrik Gmbh & Co Ohg, 5275 Bergneustadt Kupplungsscheibe mit einem Drehschwingungsdämpfer, insbesondere für Kraftfahrzeuge

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2833131A (en) * 1954-10-25 1958-05-06 Cooper Bessemer Corp Resilient coupling
US3386264A (en) * 1965-03-30 1968-06-04 Luxembourg Brev Participations Resilient couplings
US4277958A (en) * 1977-07-29 1981-07-14 Hackforth Gmbh & Co. Kg Flexible shaft coupling
US4252227A (en) * 1979-08-17 1981-02-24 General Motors Corporation Torsional vibration damper and clutch assembly
US4380442A (en) * 1980-03-15 1983-04-19 Firma Carl Freudenberg Flexible coupling
US4368050A (en) * 1980-09-08 1983-01-11 Barry Wright Corporation Coupling
US4424046A (en) * 1980-10-06 1984-01-03 Sgf Suddeutsche Gelenkscheibenfabrik, Gmbh & Co. Kg Flexible coupling

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5697261A (en) * 1993-12-23 1997-12-16 Valeo Damping device for absorbing rotation shocks, and a friction clutch including such a device
US5573463A (en) * 1994-05-20 1996-11-12 Continental Emsco Company Elastomeric drive line coupling for transmitting torque and simultaneously accomodating shaft misalignments and angular deflections
EP0992699A3 (fr) * 1998-10-09 2000-11-02 Safe Developments Limited Disque d'embrayage
US7426870B2 (en) * 2002-07-15 2008-09-23 Endress + Hauser Gmbh + Co. Kg Torsional fixing device, especially for the housing of a measuring transducer
US20060249470A1 (en) * 2005-05-06 2006-11-09 Voith Turbo Scharfenberg Gmbh & Co. Kg Separable center position coupling
US7513376B2 (en) * 2005-05-06 2009-04-07 Voith Turbo Scharfenberg Gmbh & Co. Kg Separable center position coupling
CN110247522A (zh) * 2018-03-09 2019-09-17 株式会社电装 旋转电机
CN110247522B (zh) * 2018-03-09 2022-08-02 株式会社电装 旋转电机

Also Published As

Publication number Publication date
ATE20273T1 (de) 1986-06-15
EP0090075A1 (fr) 1983-10-05
DE3271574D1 (en) 1986-07-10
JPS58178025A (ja) 1983-10-18
EP0090075B1 (fr) 1986-06-04
DE3211238A1 (de) 1983-10-06

Similar Documents

Publication Publication Date Title
US5697261A (en) Damping device for absorbing rotation shocks, and a friction clutch including such a device
KR100342282B1 (ko) 자동차용댐핑플라이휠
US5052978A (en) Elastic coupling with hydraulic damping device
US4551115A (en) Driveshaft coupling with elastomer damper
KR101972112B1 (ko) 마찰 클러치 조립체
US8262485B2 (en) Vibration damper for a drive train
US4500300A (en) Rotationally elastic coupling
PL194019B1 (pl) Amortyzator dwupierścieniowy
US8978861B2 (en) Friction clutch plate with damping springs
EP1390633B1 (fr) Dispositif d'isolation contre les fluctuations de couple
KR101195945B1 (ko) 비선형 특성을 가지는 직렬 연결 토션 댐퍼
GB2329447A (en) Torsional vibration damper with rolling coupling elements moving in slotted guide ways.
GB2329230A (en) Torsional vibration damper having couplings rolling in sprung recesses.
US4560367A (en) Torsionally elastic coupling
US4789375A (en) Spring damper drive for a clutch driven disc assembly
AU6121780A (en) Two-stage coaxial spring damper
US4504244A (en) Rotationally elastic coupling
US4499981A (en) Damper disc with concentric springs including hourglass-shaped springs to reduce the effect of centrifugal forces
US5795231A (en) Flexible shaft coupling
US3386265A (en) Torsionally resilient drive
CA1207158A (fr) Accouplement antivibrations
US6168525B1 (en) Flexible clutch for a two-mass flywheel
US5211606A (en) Transmission coupling device with composite resilient element
US6171192B1 (en) Flywheel assembly employing a damper mechanism having an annular chamber filled with a dry lubricant
JPS6357923A (ja) 弾性継手

Legal Events

Date Code Title Description
AS Assignment

Owner name: WOCO FRANZ-JOSEF WOLF & CO., SPRUDELALLEE 19, 6483

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNORS:WOLF, FRANZ-JOSEF;PLETSCH, HUBERT;REEL/FRAME:004071/0921

Effective date: 19821203

FEPP Fee payment procedure

Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

FPAY Fee payment

Year of fee payment: 4

REMI Maintenance fee reminder mailed
LAPS Lapse for failure to pay maintenance fees
FP Lapsed due to failure to pay maintenance fee

Effective date: 19930221

STCH Information on status: patent discontinuation

Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362